Mechanical movement.



R. A. NORLING.

V MECHANICAL MOVEMENT.

. PPLIOATION FILED Dno.14, 1910.

Patented May 21,1912. 2 sums-SHEET 1.

#s @Suf R; A. NORLING. MECHANICAL Mowmlxam".4

I v l APPLIOATIOI FILED DEO. 14, 1910. I

2 SHEETS-SHEET 2.

Patented May 21, 1912.

UNiTnnsTATns PATENT onirica. l

REINHOLD A. NORLINS', OF AURORA, ILLINOIS, ASSIGNOB T0 AURORA AUTOMATIC `MACHINER'Y COMPANY, 0F .AURORA7 ILLINOIS, A CORPORATION OF ILLINGIS.

MECHANICAL MOVEMENT.

Original application flied May 7, 1907, Serial No.r 372,407: Divided and this application tiled December 14,

Specification of Letters Patent.

` Patented May 21, 1912.

1910. Serial N0.`597,311.

To' all -'whom it may concern:

Be itknown that I, REINHOLD A. NoRLiNG, a citizen of the United States, and a resident of the city of Aurora, county of Kane, and State of Illinois, have invented certain new 'and useful Improvements in Mechanical Movements and I do herebyvdeclare thatthe following is a full, clear, andv exact den scription thereof, referenceA being had to the accompanying drawings, and to the letters ofreference marked thereon, which form a part of this speciiica'tion.

This invention relates to an improved mechanical movement i'or` transmitting rotative motion to a driven shaft from two reciprocating prime movers, having equal re- .ciprocatory movement, in opposite directions and in parallel paths. The invention consists in the matters hereinafter4 set forth and more particularly pointed out in the appended claims.

The mechanical movement embodying my invention is more particularly adapted for use in drilling machines, wherein the two reciprocating prime movers constitute vthe pistons in the two double-acting cylinders o t' a pneumatic motor, and the rotative driven shaft is employed for giving rotative move ment to a-drill -or like tool.

f" i Ihave illustrated'my invention in the accompanying drawings -in connection with a drilling machine of the kind stated, the

same being substantially like that shown and described in my' prior Patent No. 969,394, 'dated September 6,'1910; this application vbeing a division of thev application for said Patent, Serial Number 372,407, filed May 7, 1907. The `drilling machine shown in the accompanying drawings is also substantiallyl like that shown and described in my prior application, Serial 'Number 558,616, filedI April-30, 1910, which is also a division of said. application,` Serial No. 372,407, on whichsaid Letters Patent No. 969,394 was issued.

3. isa central vertical section of a motor'vfor -li drilling machine embodying my 'invention, said section bein 'taken axially through thedrill spindle. Fig. 2 is a cross-section, taken on line 2 2 lof Fig. 1. Fig. 3 is a longitudinal section, taken on line 3 3 of Fig. 1. Fig. 4 is a longitudinal section,

.and constituting partpof the mechanism for :driving or rotating said spindle.

In the accompanying drawings`: Figure taken von the indirectline 4 4 of Fig. 1. Fig. 5 is a transverse section, taken on line 5 5 of Fig. 4. Fig. G is a cross-section, taken Von line 6 6 of Fig. 4. Fig. 7is a detail section illustrating the valve for controlling the admission of the motive iiuid i to the motor cylinders.

As shown in said drawings, 12 designates an elongated hollow7 frame or casing in one end of which is mounted a drill-spindle 13 and to the opposite end of which is attached the power cylinders of an engine or motor.

Said, drill spindle 13 constitutes the driven` shaft of the mechanical movementconstitut-y ing my invention.l Said casing constitutes the principal part of a crank-case for the motor, and also an inclosure and support for the bearings of the drill spindle 13 and the mechanism by' which thel'drill spindle is o perated from the motor. At one end the drill spindle 13 is provided with a socket to receive the shank of the drill, and extends through the wall of the casing, turning in a bearing 14 in said wall. At its opposite end said spindle engages a bearing member 15 affixed to the adjacent wall ot the casing, as hereinafterdescribed. Said spindle is also provided, within the casing or frame, with a series of elongatedv ratchet teeth .16' ar.- ranged lparallel with the axis of the spindle The motor as herein shown has the form of a two cylinder pneumatic engine, and embraces two parallel power cylinders 17,

17 located side by side and formed in a' single casting 18 having at its inner end a flange 19 by which it is bolted or otherwise secured to the adjacent end of the casing or frame. 12, as clearly-shown in Figs. 1 and 7.

The pistons 20, 2O of said motor areconA-v' nectedby piston ,rods 21, 21 and connecting rods 22, 22 with the two cranks 23, 23 of the crank-shaft 24', which latter is mounted at its ends in the side walls of the frame 12. Said pistons ,20, 20 constitute the two reciprocating prime movers of the mechanical Amovement which forms the subject. ofI this invention. :A portion of one side wall of Athe casing is removable and constitutes a cap or closure 25, the removal of which permits access to the interior of the casing for the insertion and removal of the crank-shaft sind and its associated parts, as well as the mechanism for communicating motion from the crank-shaft to the drill spindle. The crank-shaft 24 engages at its ends ant-ifriction roller bearings 26 mounted in one side wall of the frame and in the 'opposing removable cap The saidcpiston rods have cross-heads 29 which slide in cross-head guides 30 shown in the drawings as of cylindric form. The cross-head guides are formed on plates El which constitute the inner cylinder heads and are attached by bolts to the flange 19 `on the inner end of the cylinder casino', said plates 3l and the liange 19 constituting an end wall for the end of the casing 12 adjacent to the cylinders. Said inner cylinder heads are equipped with bushings 33 through which'the piston rods slide. A

35, 35 designate valve chambers, formed in the cylinder casing and located at the opposite sides and between said cylinders. ln said cylinder casting are formed the' various ports leading to the cylinders and the supply passage for the motive fluid, as will hereinafter appear. Said valve chambers are open at their inner ends and closed at their outer ends by the end Walls of the bushings. Reciprocating in said valve chambers are piston valves, each designated as a whole by 3T. Each of said piston valves is provided with two reduced parts 38, 3S which form three longitudinally separated, cylindric enlargements, by means of which, during the reciprocation of eachva-lve, communication is afforded alternately between the inlet port 39 of said valve chamber, and ports 40, 41 communicating with the valve chamber andthe opposite ends of the cylinders, as shown most clearly in Figs. 4 and 8. 42, 43 designate exhaust ports opening into the atmosphere, one at each end of the valve chamber through apertures 42, 3, formed 5 in the casing .18, as shown in Figs. 4 and G,

and said exhaust ports are brought alternately into communication with the cylinder ports 40, 4l through reciprocation of the piston valves, as will be clear from an inspection of Fig. 7. vAs shown in Fig. 7, the valve El? is at the limit of its forward movement, and the motive fluid then enters from the supply passage 4T (Fig. 4) through the inlet port 39 and the cylinder port 4l which, in this position of the valve, is 4in direct communication with the inlet port 39 through the chamber formed between the` rearward and middle enlargements of the valve 3T. The motive. [luid flowing through said ports while said valve Il? is in the position shown in said Fig. T, enters the cylinder l? and acts cn the piston 20 therein andv causes the same to make its rearward stroke. Saidpiston 2O in its rearward movees v 1,027,214.

communicates with the exhaust port- 42 through the chamber formed between the end of the valve chamber 35 and the rearward enlargement of said valve 37. vif hen the valve 37 is mo-ved rearwardly to the limit of its movement in that direction, the rearward enlargement` on said valve closes communication between said cylinder port 40 and the exhaust port 42 and the adjacent reduced part 38 of the valve opens communication between the inlet port 39 and the cylinder port 40, while the middle enlargement on said valve 37 passes over the cylinder port 4l and opens communication between the exhaust port 43 and said cylinder port through the space between the middle and forward enlargements of the valve. In this rearward position of said valve 37, the motive fluid acts on the piston 20 in said cylinder 17, to give to said piston .its forward stroke; the exhaust then passing from the exhaust port 43. The piston valve 37 for the other cylinder 17 of the pair operates similarly to the one as described, so that the description of one will suliice for both. Said valves 37 are reeiprocated from eccentrics44 on the main crank-shaft 24 through the medium of eccentric rods 45 connected at their ends respectively with eccentric st'aps surrounding said eccentrics 44 and with the piston valves, (Fig. 4). The inlet ports :$9 of the valve chambers communicate with a cen` end with a tube 48 which is connected with the'cylinder casting by means of a screwthreaded nipple, as shown in Figs. l. 3 and 4, and through. which the motive fluid is supplied to the motor cylinders,

' A throttle valve is located within the tube 4S for controlling the llow of the motive agent therethrough. Said val ve embraces a conical valve or plug 50 adapted to engage a correspondingly shaped seat 51 formed on an annular flange within said tube. The valve member" is held normally against its seat by a Spring 52 surrounding the stein 53 of the valve member and interposed between the valve member and an inwardly facing shoulder of a nipple 55 which has screw-threaded engagement with the outer end of said tube. The said valve member is provided with an inward axial extension or stud 56, which engages at its inner end the outer end of a hollow plug 57 located within and having endwise sliding engagement with the tube 48. The valve member 50 is lifted from its seat through the medium of a sleeve 5S surrounding and having rotative movement on the tube 4S and co'nfined between the inner end of 4the nipple 5a and an annular exterior shoulder on said tube. Said sleeve is provided with an inclined slot 59, (Fig 3) through which er:l

5 7 before referred to.

tends a screw-stud 60 which Vhas screwthreaded engagement with the hollow plug The tube 48 and its surrounding sleeve constitute aliandle which is grasped by one hand of the operator in using t-he tool.v Rotation of said sleeve in one direction/operates through the action of said inclined slot on the stud 60 to slide the hollowplug 57 and throttle valve 50 outwardly and thereby open Vthe valve. Said inclined slot 59 is provided at its outer end with a transverse end portion adapted to be engaged by the stud to hold the valve closure-mits open position. The valve and mechanism for operating the same constitute no part of the present invention andthe construction and operation thereof need not be furtherherein described.

`Referringiiow to the mechanism for transmitting motion from the crank-shaft 24 to the drill spindle, said mechanism embraces two swinging levers 61, 62 disposed one over or at vthe side of the other and arranged to turn vor rotate about ,the axis ofthe drill spindle, and provided each with a pawl 66 adapted to engage the ratchet teeth 16 on the drill spindle and turn the latter, when the lever is swung or moved in one direction, and to pass over said teeth when the lever is swung in a reverse or'backward direction.

. Said levers are arranged to swing or oscileach lever being moved or swung forwardly,

late reversely in such manner that when one of the levers `1s swung 1n a direction to rotate the drill spindle forwardly the other lever is swung or moved backwardly or retracted;

l or in a direction to rotate the spindle while the other lever is being restored to its starting` point. The said. reversely swinginglevers are so connected with the mechanism which operates the same that the retracted lever i is reversed and engages the drill spindle in a manner to turn the same forwardly before the lever which is then completing its forward swing is released from the drill spindle, whereby the-rotationof the drilh ist made' continuous. The said pawl carrying levers may he pivotally supported or niounted in any suitable -way in the machine frame or casing, but, as shown in the accompanying drawings, they are provided at their outer or forward ends with hubs 67 l having smooth cylindric apertures which iit over and have bearing onthe toothed part of the drill spindle.

lThe levers are swung or vibrated through the medium of a secondary crank-shaft- 70,

iarallel with the main crank-shaft 24, and

:provided with two crank-pins 71, 72 corresponding with the cranks of the main crankshaft. The secondary crank-shaft is rotatively mounted at its 4ends in antifriction roller bearings 73, 74 mounted, `one set in one side wallof the fra-nie, and the other set inthe cap or closure 25. The said secondary Y 'crank-shaft is driven.

crank-shaft is rotated from the main crankshaft through the medium of intermeshing y gear-wheels 75 and 7G on the secondary and main crank-shafts, respectively, said gear wheels being Aarranged to drive the secondary shaft at the same speed that the primary The said klevers are provided at their inner or swinging ends with laterally separated arms 78 between which the crank-pins 71, 7 2 of the secondary crank-shaft operate. Said fork-arms 78 of the pawl hearing levers have smooth inner parallel bearing surfaces, and the crankpins 71', '72 of the secondary crank-shaft are provided with bearing blocks 80, 80, (each made of two halves or parts to facilitate the fitting thereof over the crank-pins) which have smooth side or lateral faces for engagement with the inner faces of the fork arms of said pawl-bearing levers. It is obvious that the enlargement of the crank-pins of the secondary crank-shaft will produce the saine e'ect as the bearing blocks describedgbut, for convenience of manufacture and to increase durability, the separate bearing blocks are preferred.

The operation of the secondary crankshaft, acting through the pawl bearing levers and their pawls to continuously rotate the drill spindle is as described in my said application No. 558,615 rEhe pawl and ratchet driving connection between the vibrating levers and the drill spindle or driven shaft,

made as hereinbefore set forth, affordsa i chanical moveii'ient, may be obtained when, in place of said pawl and ratchet connection,

is employed some other well known form of connecting means analogous in character to a pawl and ratchet mechanism, adapted to transmit, from the vibrating levers, turning movement to the drill spindle, constantly in one direction.

Inasmuch as the secondary crank-shaft 7() rotates in the direction indicated by the ar- .row in Fig. 3 and each crank-.pin thereof rotates, during its power stroke, in the arc,

farthest away from the drill spindle, it will be seen that the greatest force of the pawl bearing devices is exerted in mid-position as shown iiiFig. 3, and the greatest power is required to-turn the drill spindle, asit is then moving' at its maximum speed. The lever is, however, at this time exerting its greatest leverage because its associated crank-pin of the second secondary crankp shaft is at the same time operating on the part of the lever farthest from the spindle.

I arrange the crank-pins on said Amain crankshaft atsuch angular distancesapartv that saidcraiik-shaft exerts its greatest power to .form power throughout the full rotation of the crankshaft and further that if the crankpins be placed at 180 degrees apart, the

- power of the two pistons will be exerted simultaneously with the result, however, that both crank-pins will be simultaneously on a dead center at the end of each stroke. In order to more effectively transmit power from the two pistons to the vibrating levers I arrange the crank-pins of the main crankshaft so that the pistons act on both of said crank-pins when the. latter are in position requiring the greatest power to turn the same, to wit, when the crank-pins of the secondary crank-shaft are passing through that part of their circular path farthest from the axis of oscillation of the levers.

s shown in the accompanying drawings, the crank-pins of the main crank-shaft are placed at` approximately 135 degrees apart, as indicated in Figs. 3 and et, and as a result, when the paw] bearing lever, which is making its driving or power stroke, is at midposition, both of the crank-pins of the main crank-shaft are in position to receive maximum power from the pistons acting thereon. As shown in F ig. 4, the pawl bearing levers are at the limits of their vibratory movement. In this position one of the ycrankpins of the main crank-shaft has just passed lthe dead center while the other crank-pin is approaching its dead center. lVlien, however, the parts are in the position shown in Fig. and one of the vibratory levers is in the n'iiddle of its advance or power stroke and the other is being retracted, one of the crank-pins of the main crank-shaft will be approaching the point in its path at which the crank-shaft receives maximum power from its associated piston. while the other crank-pin will have passed such point. It follows that the work of impelling each lever, during the power or driving stroke of -the same will be divided between, or )articipated in by, both pistons. That is to say,

one of the crankpins of the main crank-I shaft will come into such position that its associated piston will exert its maximum driving power on the crank shaft when one of theV levers is approaching', and until it reaches, a point midway of its power stroke, and the other crank pin will then come immediately into such position that its associated piston will exert its maximum power on'the crank shaft, to complete the power stroke of such lever. The constructionv described, therefore, has the advantage that the two pistons act conjointly and suc'cesshaft crank pins will be in position for thel action of its associated piston during the effective part of the stroke of said piston, when the other crank pin is on 4its dead center. i

The construction of t'hetool spindle and its bearings in the frame or casing is the same as set forth in my prior Patent No. 969,394. One wall of the casing or frame is provided with a bushing 100 which constitutes the bearing for the lower cylindric portion of the spindle. On the upper or inner end of the said drill spindle is mounted a ring or collar, constituting the rotative member of a thrust bearing, the non-rotative member of which consists of an annular flange 108, formed on a tubular bearing member 105, which is secured in the top wall of the casing in axial alinement with the drill spindle by means ofI a locking ring 102 which has screw-threaded engagement with the surrounding casing wall and clamps the flange 103 against an upwardly facing shoulder on said wall. Atifriction balls 104 are interposed between the rotative ring 101 and the flange 103. The hubs of the levers 61 and 62 are confined between and held from movement endwise of the drill spindle by contact with the bushing 100, and the ring 101. The sleeve 105 is extended downwardly or inwardly to form an externally cylindric bearing member 106 which fits within a cylindric bearing recess formed in the upper end of the drill spindle. The bearings for holding the spindle laterally in place thus comprise the exterior bushing 100 at its lower end and the interior extension 10G of the-fixed sleeve 105 at its upper end. The upward end thrust of the tool spindle is resisted by the thrust-bearing formed by the ring 101, the flange 10?, and the balls 104. The said tool spindle is held from downward endwise movement by an annular shoulder 107 thereon, which bears against the upper or inner end of the bushing `100.

The upper sleeve 105 isy made hollow and interiorly screw-threaded to receive a feedscrew 108 by which the drill is fed to its work, in a familiar manner. The said feedscrew is providedat its inner end with an axial projection 100 that extends through an aperture in a transverse diaphragm or wall 110 that constitutes the stop for the drill shank, said extension 109 being adapted to engage the drill shank in a manner to eject the same from the tool holder.

As will be understood from the foregoing,

vthe two pistons in the Adelible-acting cyliA ders of the pneumatic rnotor illustrated .and on financie described, constitute the prime movers'of a mechanical movement designed Y for eiii;y ciently transmitting movement fromA snc prime movers to a constantly rotating driven shaft, which constitutes my invention, and, in the embodiment of a' mechanical' moveinent, made in accordance with'v my inveninvention being to provide such a construction in a mechanical movement or motiontransmitting device, of this kind, that the two prinie. movers will vact conjointly and successively to exert maximum turning power on the driven shaft or spindle during the timethat each swinging lever is acting on the driven shaft or spindle in making its dri-ving o'i power stroke.

I claim as my inventionz" 1L The combination with two prime movers having reciprocating motion through equal distances in opposite directions inparallel paths, and al driven shaft, of a primary crank shaft provided with two crank pins with which said prime movers are severally connected, two swinging actuating levers, means affording driving connection. between each actuating lever and said. driven shaft during each stroke of the actuating I lever in one direction, and.' an intermediate or secondary crank shaft arranged parallel with said primary crank shaft and the driven shaft and provided with crank pins located at equal angular -distances apart and severally acting on said swinging actuating levers, said crank pins and actuating levers being so arranged that the forward or driviiig-stroke of each actuating lever is effected in the movement of the crank pin acting y thereon through the part of its path-remote from the driven shaft, and caring connecting said priniarycrank shaft with said secondary crank shaft, said primary crank shaft having its crank pins arranged at less than 1800' apart and so arranged with relation tothe crank pins of the secondary crank shaft that power to turn said primary crank shaft' is exerted onA the: latter by both prime movers during the time each actuating lever is making its power or driving stroke.

2L The ,i combination with two prime movers having reciprocating motion through equal distances in opposite -directions in par-` i, allel paths, and a driveI i Lsha ft,,of a primary withJwh-ilch, said'pifinie mcvers'are severally connected, two swinging actuating levers,

means affording driving connection between' each actuating lever and said driven shaft during each strokeof the actuating lever `in one direction, and an intermediate or secondary crankshaft arranged parallel with said 'primary crank shaft and the driven shaft andprovidedwith crank pins located at equal angular distances apart and lseverally acting on said swinging actuating levers, said crank pins and actuating levers being so arranged that the forward or driving stroke of each actuating lever is effected in the movement of the crank vpin acting thereon through the part offits path remote from the driven shaft, and gearing connectthan 180 apart 4and in such angular relation to each other that when one crank pin ing said primary crank shaft with said sec#A ondary cran shaft, the crank pins of said primary crank shaft being arranged at less 8.5

is on a dead center the other crankpin will 7 be in driving position, and said crankLpins i of the primary crank shaft being arranged iii such relation to 'the crank pins of thesecondary crank shaft that power for turning ,y said primary crank shaft is exerted on the latter by both prime movers when leach actuating leverfis making its power or driving stroke. c

A 3. The combination with two prim'iiig'yers having reciprocating motion through equal distances in opposite directions in Y,

parallel paths, and a driven sha-ft,gof a primary crank shaft provided with two ico' crank pins with which said prime movers are severally connected, two lswinging actuating levers, means affording driving connection .between each actuating lever and said driven shaft during each stroke of the actuating lever in one direction,

and an intermediate or secondary crank i shaft arranged parallel with said primary crank shaft and the driven shaft and provided with crank pins located at equal angular distances 'apart and sev-' erally acting on said swinging actuating levers, said crank pins and actuating levers being so arranged that the forward or driving stroke of each actuating lever is effected in the movement of thecrank pin acting thereon through the part of its path remote from the driven shaft, and gearing connecting said primary crank shaft with said secondary crank shaft,the crank pins on said primary crank shaft being so arranged rela- 1- t-ively to each other 'that when'one crank pin'is on its dead center the other crank pin will be in driving position, and the crank pins of said primary crank shaft being so arranged relatively to each other and tov those of the secondary crank shaft that said crank pins of thel primary-crank shaft will come successively into driving position and the primevgmoiers willw-atfconjeintly to eX- ert power on the primary crank shaft duringthe time each actuating lever is making its power or driving stroke.

1l. The combination with two prime movers having reciprocating motion through equal distances in opposite directions in parallel paths, and a driven shaft, of a primary crank shaft provided with two crank pins w'th' which said prime movers `are severally connected, two vswinging actuating levers, means affording driving connection between each actuating lever and said driven shaft during each stroke of the actuating lever in one direction, and an intermediate or secondary crank shaft arranged parallel with said primary crank shaft and the driven shaft and provided with crank pins located at equal angular distances apart and severally acting on said swinging actuating levers, said crank pins and actuating levers being so arranged that the forward or driving stroke of each actuating lever is etlectcd in the movement of the crank pin acting` thereon through the part of its path remote from the driven shaft, and gearing connecting said primary crank shaft with said secondaryT crank shaft, said primary crank shaft having its two crank pins located at approximately 135 apart and arranged in such relation lto the crank pins on the secondary crank shaft that power is exerted by both of the prime movers on said primary crank shaft during the time each actuating lever is making its power or 'driving stroke.

In testimony, that I claim the foregoing as my invention l atlix my signature in the presence of two witnesses, this 9th day of December, A. D. 1910.

REINHOLD A. NORLlNG.

Witnesses:

C. A. BUnonss, ALois C. l/VARKEN. 

